RU2309316C2 - Distance ring - Google Patents

Distance ring Download PDF

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Publication number
RU2309316C2
RU2309316C2 RU2003125915/06A RU2003125915A RU2309316C2 RU 2309316 C2 RU2309316 C2 RU 2309316C2 RU 2003125915/06 A RU2003125915/06 A RU 2003125915/06A RU 2003125915 A RU2003125915 A RU 2003125915A RU 2309316 C2 RU2309316 C2 RU 2309316C2
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RU
Russia
Prior art keywords
sealing
characterized
sealing body
gasket ring
annular groove
Prior art date
Application number
RU2003125915/06A
Other languages
Russian (ru)
Other versions
RU2003125915A (en
Inventor
Андреас ШЛЕТ (DE)
Андреас ШЛЕТ
Винфрид ШУЛЬЦ (DE)
Винфрид ШУЛЬЦ
Ханс-Вальтер БРЕННЕР (DE)
Ханс-Вальтер БРЕННЕР
Original Assignee
Фесто Аг Унд Ко
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to EP02018818.1 priority Critical
Priority to EP02018818A priority patent/EP1391640B1/en
Application filed by Фесто Аг Унд Ко filed Critical Фесто Аг Унд Ко
Publication of RU2003125915A publication Critical patent/RU2003125915A/en
Application granted granted Critical
Publication of RU2309316C2 publication Critical patent/RU2309316C2/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16LPIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/001Screw-threaded joints; Forms of screw-threads for such joints with conical threads
    • F16L15/003Screw-threaded joints; Forms of screw-threads for such joints with conical threads with sealing rings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/02Sealings between relatively-stationary surfaces
    • F16J15/06Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/061Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with positioning means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/02Sealings between relatively-stationary surfaces
    • F16J15/06Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/10Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
    • F16J15/104Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing characterised by structure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16LPIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/006Screw-threaded joints; Forms of screw-threads for such joints with straight threads
    • F16L15/008Screw-threaded joints; Forms of screw-threads for such joints with straight threads with sealing rings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16LPIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00Flanged joints
    • F16L23/16Flanged joints characterised by the sealing means
    • F16L23/18Flanged joints characterised by the sealing means the sealing means being rings
    • F16L23/22Flanged joints characterised by the sealing means the sealing means being rings made exclusively of a material other than metal
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16LPIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L41/00Branching pipes; Joining pipes to walls
    • F16L41/08Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of the wall or to the axis of another pipe
    • F16L41/10Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of the wall or to the axis of another pipe the extremity of the pipe being screwed into the wall

Abstract

FIELD: mechanical engineering, in particular, distance rings.
SUBSTANCE: distance ring has circular major part designed for substantially maintaining of constant shape and comprising circular channel provided on at least one axial side thereof and adapted for holding of sealing body from rubber elastic material. Sealing body axially protrudes with its sealing thickened portion above major part. Holding capacity of circular channel at least corresponds to volume of sealing body so that on loading and deformation of sealing thickened portion circular channel is capable of receiving material of sealing body.
EFFECT: provision for producing of reliable sealing of joints.
12 cl, 9 dwg

Description

The invention relates to a spacer ring with an annular main part essentially maintaining a constant shape, which comprises an annular groove concentrically placed on at least one axial side with two radially opposite lateral surfaces of the groove, in which an annular part consisting of a rubber elastic material is fixed, which has protruding axially above the main part of the sealing thickening.

A gasket ring of this type, known from EP 0922888 A2, has a main part consisting of a thermoplastic synthetic material, on the axial side of which a sealing body made of an elastomeric synthetic material is placed concentrically to the main body part. The sealing body is located in the annular groove of the main part and the sealing thickening protrudes from the annular groove and along the axis above the main part. In use, the spacer ring can be mounted axially between two sealing surfaces of two parts that are sealed relative to each other, and the sealing thickening, when both parts are clamped together, is loaded with one sealing surface and is deformed. In this way a sealing contact is created between the corresponding part and the sealing body.

If both parts to be joined are tightened too hard, the sealing body may be destroyed due to too much compression. In particular, there is a danger that the sealing lip will be cut off in whole or in part. In order to counter these difficulties, it has already been proposed in DE 3918891 C2 to place a sealing body on an oriented radially inner surface of the L-shaped main part. The main part serves in this case as a hard stop to limit mutual rapprochement of the parts connected to each other so that flattening of the sealing body is prevented. The sealing body itself can also deviate radially inward, which, however, leads to the fact that the increase in opposing forces is limited and, therefore, the pressure between the sealing surface and the sealing body of the spacer ring is not very high.

An object of the present invention is to provide a spacer ring of the aforementioned type, in which, in combination with a high sealing quality, the risk of damage to the sealing body is reduced.

To solve this problem, it is provided that the capacity of the annular groove at least corresponds to the volume of the sealing body so that the annular groove in the state when loading and deformation of the sealing thickening also accept the material of the sealing body determining the thickening.

Thus, the sealing thickening can, when loaded with the part interacting with it for sealing, be forced out into the annular groove, the capacity of which is chosen such that the entire volume of the incompressible sealing body finds a place in it. This prevents flattening of the sealing body. Since the sealing thickening is pressed into the annular groove, on both sides of which radial side surfaces are made, the material of the sealing body nevertheless creates an obstacle for complete movement, therefore, the opposing force sufficient for reliable contact of the seal increases. The sealing body undergoes a certain and allowable deformation in the annular groove of the main part. When tightening the sealed part tightly, it is possible, moreover, due to the greatly increased resistance when the part collides with the main part consisting of harder material, to obtain a state in which the sealing body is completely pushed into the annular groove. Similarly, the final final tight tightening of the component following this can be done with a controlled force that provides the necessary bond strength and at the same time prevents damage to the spacer ring. Since the sealing body is not damaged when using the gasket ring, the gasket ring can be used, as a rule, repeatedly.

Advantageous embodiments of the invention result from the following auxiliary claims.

The lateral surfaces of the annular groove are suitably beveled so that they tend to converge with each other in the direction of the depth of the groove. In the area of the groove of the groove, the annular groove has preferably a larger width than the portion of the bottom of the groove.

In order to ensure the necessary capacity of the annular groove inside the annular groove, an annular space is preferably provided radially on each of both sides of the sealing lip, respectively, for receiving the deformed material of the sealing lip. These annular spaces are preferably delimited radially, on the one hand, by a sealing thickening and, on the other hand, by the lateral surface of the groove relating thereto. This can be done, in particular, by means of the fact that the sealing body has a base section adjacent to the bottom of the groove and resting on the side surfaces of the groove, which has an oversized thickening in comparison with the width of the annular groove along the axis.

The inner free space provided radially inside the sealing lip preferably has a larger cross-section than the outer free space provided radially outside the sealing lip. In addition, preferably the inner free space is made with greater depth compared to the outer free space. The internal free space in the area of the pharynx of the groove may also have a greater width than the external free space. Each of these measures favors the process of deformation of the sealing thickening so that it directionally bends more radially inward than radially outward if it is axially loaded by the sealing surface of the sealing part. Due to this, it is particularly effectively prevented that the sealing thickening is pushed out radially outward from the annular groove and thereby is possibly located between the sealing surface of the part and the main part. Thus, they achieve better reliability from damage to the sealing body.

Preferably, both the main body and the at least one sealing body are composed of synthetic material. A thermoplastic synthetic material is recommended as the material for the main part, and an elastomeric synthetic material as the material for at least one sealing body. Preferably, the corresponding sealing body is molded on the main body by injection molding.

If the spacer ring on both axial sides is equipped with a sealing body located in a suitably made annular groove, then both sealing bodies can be molded separately from each other on the main part, but there is also the possibility of one-piece manufacturing if the main part is provided with connecting connecting between the two ring grooves channels through which elastomeric material of the sealing body can pass during injection molding, so that both manufactured sealing materials la result connected to each other by bridges of material in one piece.

In the area of its inner circumference, the spacer ring preferably has several circumferentially distributed retaining protrusions made integrally with at least one sealing body and protruding radially inward with respect to the main part. The locking projections in use can ensure that the gasket ring is fixed without the possibility of loss when, for example, it is worn on the external thread of the screw part. In this case, the locking protrusions can have a centering effect and prevent lateral displacements of the spacer ring relative to the sealing part.

The gasket ring is suitable for use, in particular, for sealing two axially facing each other sealing surfaces provided on two parts connected by twisting. One of the parts can be a screw part, for example, a plug or a threaded connection, having a threaded pipe part provided with an external thread, screwed into the internal thread of another part, for example, a valve or a working cylinder. In this case, the spacer ring is axially threaded onto the threaded part, and the existing locking projections provide locking on the threaded part.

Below the invention is explained in more detail using the attached drawings. They are showing:

figure 1 - the preferred structural form of the cushioning ring according to the invention in section with an axially and radially extending section plane in accordance with line 1-1 of figure 2, wherein two fluid tightly connected parts are schematically indicated by a dot-dash line,

figure 2 - cushioning ring of figure 1 in a top view with an axial direction of view along arrow II of figure 1,

figure 3 is a partial image of the spacer ring of figure 2 with the direction of view along arrow III in the area of the locking protrusion,

figure 4 is an external view of the spacer ring of figure 2 with a direction of view along arrow IV at the site of the casting site for injection molded sealing bodies,

figure 5 - in an enlarged partial image, the cross section of the spacer ring of figure 2 in accordance with the section line V-V, and shows the initial state,

6 is a view, comparable to FIG. 5, of a cut-out of a spacer ring in a state in which the component to be sealed was manually tightened with a small force until it touches the spacer ring on the main part,

Fig.7 - in the corresponding figure 5 and 6, the image of the cutout of the spacer ring from figure 2 in a state in which the sealed part is pre-pulled to the maximum required load to the spacer ring,

Fig. 8 shows, in the corresponding view of Fig. 1, an alternative structural form of the spacer ring without the image of the parts being sealed and in the context with the axis of the cut along the axis and radially along the line VIII-VIII of Fig. 9,

Fig.9 is a bottom view of the spacer ring of Fig.8 with the direction of view along arrow IX.

Figure 1 shows the dash-dotted line in the schematic image of the two connected to each other hermetically for liquids details 1, 2 in cross section. The first part 1 has a recess 3 in the form of a channel provided with an internal thread. The second part 2 has a threaded part 4 made, for example, in the form of a rod or nozzle, equipped with an external thread coordinated with the internal thread of the recess 3. Thus, the threaded part 4 can be screwed into the recess 3, and it is displaced relative to the first part 1 in the direction of movement indicated by the arrow.

At the axial end of the threaded part 4, the second part 2 comprises an annular protrusion 6 radially protruding from the threaded part 4. It can be formed, for example, by the actuation section of the second part 2, which allows you to put on a screwing tool.

In the state of the threaded part 4 screwed into the recess 3, the annular surfaces of the seal 1, 8 provided on the parts 1, 2 are axially opposite to each other. The first annular surface of the seal 7 is located on the first part 1 at the peripheral portion of the inlet of the recess 3. The opposite second annular surface of the seal 8 is radially outside the threaded part 4 on the side of the annular protrusion 6, which is axially directed to the first part 1.

The second part 2 of the exemplary embodiment is formed by a plug screwed into the recess 3 in order to close it with a liquid seal. Moreover, for the first part 1, we can talk about parts containing a fluid, such as compressed air or oil. Thanks to the screwed-in plug, the medium escapes.

In another embodiment not shown in more detail, part 2 forms a connecting part having a through channel and connected to or connected to a further rigid or flexible conduit for the working medium. In this case, in the state screwed into the first part 1, a fluid connection is created between the channel-shaped recess 3 and through the second part 2 a pipeline for the working medium placed on it. The latter is a typical application in the sector of pneumatics or hydraulics, and for the first part 1 we can talk, for example, about a valve or a drive driven by the force of the working medium.

To seal both parts 1, 2 relative to each other according to the invention, a spacer ring 12 is provided. Figs. 1-7, on the one hand, and also Figs. 8 and 9, on the other hand, show two preferred embodiments of this spacer ring 12. B in the assembled state, the spacer ring 12, as shown in FIG. 1, is mounted axially between the two sealing surfaces 7, 8 of the two parts 1, 2 that are sealed against each other. The threaded part 4 is inserted through the spacer ring 12 sie.

On each of its two axial sides oppositely directed along the axis, the spacer ring 12 has an annular sealing portion 13, 14. In the operating position shown in FIG. 1, the first sealing portion 13 faces the first surface of the seal 7, and the second sealing portion 14 faces the second surface seals 8. To establish a tight connection, the second part 2 is then screwed with a sufficient moment of rotation into the recess 3 so that the above-mentioned sealing segments 13, 14 are loaded by the annular surfaces of the seal 7, 8 on axially directed pressure. This pressure exerts a compaction effect, which, as required, prevents the medium from escaping between the two parts 1, 2.

Preferably, the spacer ring 12 is composed of several elements molded to each other by injection molding into an integrated unitary assembly. In the exemplary embodiment, these elements are an annular main part 15 and two also annular sealing bodies 16. The bodies, as follows from FIGS. 2 and 9, are mounted concentrically to each other.

On each axial side of the main part 15 there is one of the sealing bodies 16. Each sealing body 16 is fixed in an annular groove 25 made on the corresponding axial side in a concentric orientation in the main part 15. Preferably, both ring grooves have the same diameter and the same cross-sectional contour.

As can be clearly seen in FIGS. 5-7, each annular groove has grooves oriented along the axis 52 and two radially opposite inner and outer lateral surfaces 53, 54 of the groove. The sealing body 16, the lower section 26 is located in the corresponding annular groove 25 and protrudes - if you look in the initial state in figure 1, 8 and 5 - sealing thickening through the mouth 55 of the groove along the axis of the annular groove 25 and thereby goes axially over the main part 16.

The lower portion 26 of the sealing body 16 is suitably adjacent to the bottom 52 of the grooves and at the same time rests on both side surfaces 53, 54 of the groove. The sealing collar 24 has, in particular, a smaller width as compared with the lower portion 26 and the width of the annular groove 25, therefore, its portion located in the annular groove 25 is spaced from both side surfaces 53, 54 of the groove.

The main part 15 largely maintains the constancy of the shape of the spacer ring. It preferably consists of a thermoplastic synthetic material. Essential to the seal are both of the sealing body 16, each consisting of an elastomeric synthetic material. The manufacture of the spacer ring 12 can be carried out, in particular, as part of a method for injection molding of two-component materials. In this case, the main part 15, preferably made of stiffer synthetic material, is firstly cast, after which both sealing bodies 16 are molded simultaneously or successively by applying the corresponding synthetic material.

Although it would be possible to make the spacer ring 12 so that it had only on the axial side a sealing body 16 with the properties of a rubber elastic material. Sealing on the other axial side could be carried out by other measures, for example, one or more annular protrusions on the main part 15. But preferred are embodiments provided with a sealing body on both axial sides.

The annular grooves 25 are made so that their capacity corresponds to at least the volume of the corresponding sealing body 16. A structural shape in which the capacity of the annular groove 25 is equal to or slightly larger than the volume of the corresponding sealing body 16 is preferred, as is the case in the exemplary embodiments.

Due to such a coordinated arrangement, it is achieved that the annular groove 25, when loading and deforming the sealing lip 24 of the corresponding sealing body 16, can also accept the sealing lip material 24 defining the sealing lip 16. This is explained using FIGS. 6 and 7, showing the cut-out of the sealing body 16 under different load conditions.

If the spacer ring 12 is brought into the working position between both parts 1, 2, then the sealing body 16 first assumes the initial position shown in FIG. 5, in which it protrudes beyond the main part 15 with the sealing thickening 24. If now the second part 2, for example, in the screwing process moves in the direction of movement 5 to the main part 15, then the second seal surface 8 provided on it presses on the sealing lip 24 and deforms it into a sufficiently large annular groove 25. In this case, FIG. 6 shows There is a state in which the second part 2 is screwed in manually until it, with its second sealing surface 8, comes into contact with the end surface 56 of the main part 15 adjacent to the throat 55 and already in this intermediate position, the sealing body 16 is completely pushed into the annular groove 25.

To reach the end position, the second part 2 is then tightly tightened with the required torque. In this case, the main part 15 is slightly deformed, and also the sealing body 16 experiences repeated loading so that it at least approximately fills the volume of the annular groove 25. In this case, the curved second seal section 14 is initially smoothed out and passes along with the adjacent end surface 56, moreover, it is on a large surface adjacent to the surface of the seal 8 of the second part 2.

Since the material of the sealing body 16, although it has entered completely into the annular groove 25, nevertheless rests on the bottom of the groove 52 and both side surfaces 53, 54 of the groove, the sealing body 16 can create a counteracting force with which its second sealing portion 14 is relatively pressed against the second surface of the seal 6. This ensures greater contact seal and higher quality seal.

Figures 5-7 show only one of the sealing bodies 16 of the spacer ring 12. The proportions on the other sealing body 16 not shown and the first part 1 interacting with it are corresponding and pass synchronously.

The lateral surfaces 53, 54 of the groove are preferably inclined, and they converge to each other in the direction of the depth of the groove shown by arrow 57. The annular groove 25 has a width greater than that of the groove bottom 52 in the groove portion of the groove 54.

To provide the sealing lip 24, the necessary space for deformation inside the corresponding annular groove 25 on both sides of the sealing lip 24 is respectively provided with a free space 58, 59. The free spaces 58, 59 receive the deformed material of the sealing lip 24.

The free spaces can in principle be formed by the recesses of the sealing body 16 in the form of grooves so that they are both radially outward and radially inside limited by the material of the sealing body. But the structural form implemented in the examples was more preferable, in which the free spaces 58, 59, although limited on the one hand by the sealing bulge 24 and thereby the material of the sealing body 16, but on the other hand, by the corresponding inner and outer side surfaces 53, 54 of the groove. This is particularly evident in FIG.

Both free spaces 58, 59 arranged concentrically with respect to each other are made so that the inner free space provided radially inside the sealing lip 24 has a larger cross-section than the outer free space 59 provided radially outside the sealing lip 24. The related cross-sectional shape the sealing body 16 causes the action that the sealing thickening 24 with an axial load is bent around facing the surface at lotneniya 7, 8 is preferably in a direction towards the inner free space 58 of larger cross section. Since with the parts 1, 2 screwed to each other, the sealing lip 24 is more likely to be forced out, thereby preventing the displacement process, and it is effectively prevented that the sealing lip 24 is forced out to the end surface 56. Thus, the sealing lip 24 cannot be clamped between the end surface 56 and facing the surface of the seal 8.

In the embodiment of FIGS. 1-7, the internal free space 58 is made deeper than the external free space 59. At the same time, the internal free space 58 is wider than the external free space 59. The latter also applies to the spacer ring 12 of FIGS. 8 and 9, in which, however , both free spaces have approximately the same depth.

The annular groove 25 and the sealing body 16 fixed therein have a constant cross section along their entire length. The cross-sectional area of the annular groove 25 is at least the same as the cross-section of the sealing body 16 in the initial state, but it is preferably at least slightly larger than the cross-section of the sealing body 16.

In all examples, the sealing bodies 16 are connected tightly to each other by mutual sputtering by injection molding.

In the embodiment of FIGS. 1-7, both sealing bodies 16 are made separately from each other. They are formed independently of each other on the main part 15. At the local location of its perimeter, the main part 15 has recesses 62 on the axial side, which are casting places for the injection molding process and in the finished state of the spacer ring 12 filled with material of the sealing body 16.

Also, in the gasket ring in accordance with FIGS. 8 and 9, both sealing bodies 16 can be manufactured by respective casting points independently of each other. As a rule, a single casting point 62 is sufficient, since other measures have been taken to ensure that the synthetic material passes between both axial sides of the main part 15. These measures consist of a large number of connecting channels 63 extending through the main part 15 in the axial direction and connecting both ring grooves 25 among themselves. They expediently end each at the bottom of the 25th groove. The connecting channels 63 are preferably distributed evenly along the length of the perimeter of the main part 15.

In injection molding, the synthetic material defining the sealing body 16 is fed through a recess 62 ending in an annular groove 25. The material fills the annular groove 25 and simultaneously passes through the connecting channels 63 to another annular groove 25, which is also filled in accordance with the required shape. In the finished state, both sealing bodies 16 are thereby joined together by means of synthetic bridges 64 passing through the connecting channels 63.

By means of the bridges of the material 64, an even better fixation of the sealing bodies 16 is achieved on the main body 15. By the bridges of the material 64, respectively, the sealing body 16 is held by the opposing sealing body 16 in the annular groove.

Preferably, the spacer rings 12 have, on a portion of their inner circumference, several circumferentially distributed retaining protrusions 33, which serve to hold the spacer ring 12 in position on the threaded portion 4 or a comparable part. Additionally or alternatively, the locking protrusions can also serve to maintain the required relative concentric position between the spacer ring 12, on the one hand, and the sealing surfaces 7, 8 of parts 1, 2, on the other hand. The locking protrusions 33 serve in this case for centering.

The locking protrusions 33 are made integral with respectively one sealing body 16 and protrude above the main part 15 radially inward. If the spacer ring 12, as in the exemplary embodiments, has two sealing bodies 16, it is sufficient that the locking protrusions 33 are provided on only one sealing body 16. They can be applied simultaneously by injection molding of the corresponding sealing body.

In the area of the locking protrusions 33, the sealing body 16 has recesses 65 on the corresponding axial side that provide radial passage of the locking protrusions 33 from the annular groove 25 to the interior of the spacer ring 12 without material exit over the end surface 56 of the main part 15.

Since the locking protrusions 33 consist of a rubber elastic material, they do not interfere with the installation of the spacer ring 12 on the threaded part. The spacer ring 12 can, with temporary elastic deformation of the locking protrusions 33, be easily axially mounted, a screwing process is not required.

The distribution of the locking protrusions 33 around the perimeter of the spacer ring 12 is reasonably uniform, and in the case of exemplary embodiments, there are respectively three locking protrusions 33.

In all exemplary embodiments, both free spaces 58, 59 do not reach the bottom of the annular groove 25. The surface of the bottom 65 of the free spaces is determined by the lower portion 26 occupying the entire width of the annular groove. As indicated by the dot-dash line 66, there is also a preferred possibility to make the internal free space 58 so so that it extends over the entire depth of the annular groove 25. Thus, in the initial state, there is no contact between the sealing body 16 and the inner side surface 53 of the groove.

In all exemplary embodiments, the free spaces 58, 59 are preferably dimensioned such that the material of the sealing body 16, when the sealing body 16 is fully installed in the annular groove 25, abuts both the bottom 52 of the groove and both radial side surfaces 53, 54 of the groove, and therefore have a support.

The particular features of the described exemplary embodiments may be combined or replaced in any way.

Claims (12)

1. A gasket ring with an essentially constant shape annular main part (15) having at least one axial side a concentrically arranged annular groove (25) with two radially opposite lateral surfaces (53, 54) of the groove, which is fixed to the sealing body consisting of a rubber elastic material (16), provided with a sealing thickening protruding axially above the main part (15), characterized in that the capacity of the annular groove (25) at least corresponds to the volume of the seal of the body (16) so that the annular groove (25) under load and deformation of the sealing lip (24) is also able to accept the material of the sealing body (16) that defines the sealing lip (24) and inside the annular groove radially at least on one side and preferably, an annular free space (58, 59) is provided on both sides of the sealing lip (24) to accommodate the deformed material of the sealing lip (24), the inner radially provided inside the sealing lip (24) vobodnoe space (58) has a larger cross-section compared with the intended radially outside the sealing bead (24) the outer free space (59).
2. A gasket ring according to claim 1, characterized in that the annular groove (25) in the section of the throat of the groove (55) has a larger width than in the section of the bottom (52) of the groove.
3. A gasket ring according to claim 1 or 2, characterized in that each free space (58, 59) is limited radially from one side by a sealing thickening (24) and from the other side by a corresponding lateral side (54.55).
4. A gasket ring according to any one of claims 1 to 3, characterized in that the inner free space (58), at least in the area of the throat (55) of the groove, has a larger width compared to the outer free space (59).
5. A gasket ring according to any one of claims 1 to 4, characterized in that the sealing body (16) has grooves adjacent to the bottom (52) and a lower portion (26) which rests on both side surfaces (53, 54), from which sealing thickening (24) having a smaller width compared to the width of the annular groove (25).
6. A gasket ring according to any one of claims 1 to 5, characterized in that the main part (15) and at least one sealing body (16) are made of synthetic material.
7. Gasket ring according to any one of claims 1 to 6, characterized in that the main part (15) consists of a thermoplastic material.
8. A gasket ring according to any one of claims 1 to 7, characterized in that at least one sealing body (16) consists of an elastomeric synthetic material.
9. A gasket ring according to any one of claims 1 to 8, characterized in that in the area of its inner circumference there are several retained protrusions (33) arranged distributed around the circumference, which are made integral with at least one sealing body (16) and protrude relative to the main part (15) radially inward.
10. A gasket ring according to any one of claims 1 to 9, characterized in that on both axial sides of the main part (15) a sealing thickening is installed in a suitably made annular groove (25).
11. Gasket ring according to claim 10, characterized in that both sealing bodies (16) are made separately from each other.
12. A gasket ring according to claim 10, characterized in that the two sealing bodies (16) are connected together by material bridges (64) passing along the axis through the main part (15) in places distributed around its circumference.
RU2003125915/06A 2002-08-23 2003-08-22 Distance ring RU2309316C2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP02018818.1 2002-08-23
EP02018818A EP1391640B1 (en) 2002-08-23 2002-08-23 Sealing ring

Publications (2)

Publication Number Publication Date
RU2003125915A RU2003125915A (en) 2005-02-27
RU2309316C2 true RU2309316C2 (en) 2007-10-27

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BR0303420A (en) 2004-09-08
HU0302705A3 (en) 2005-03-29
US6854739B2 (en) 2005-02-15
HU0302705D0 (en) 2003-10-28
EP1391640A1 (en) 2004-02-25
CZ303737B6 (en) 2013-04-17
EP1391640B1 (en) 2005-02-23
CZ20032276A3 (en) 2004-12-15
HU228786B1 (en) 2013-05-28
BR0303420B1 (en) 2014-03-04
CN1333188C (en) 2007-08-22
CN1485559A (en) 2004-03-31
US20040036233A1 (en) 2004-02-26
DE50202326D1 (en) 2005-03-31
HU0302705A2 (en) 2004-05-28
RU2003125915A (en) 2005-02-27
AT289661T (en) 2005-03-15

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